EP3376050B1 - Groupe pompe centrifuge - Google Patents

Groupe pompe centrifuge

Info

Publication number
EP3376050B1
EP3376050B1 EP17160831.8A EP17160831A EP3376050B1 EP 3376050 B1 EP3376050 B1 EP 3376050B1 EP 17160831 A EP17160831 A EP 17160831A EP 3376050 B1 EP3376050 B1 EP 3376050B1
Authority
EP
European Patent Office
Prior art keywords
valve element
impeller
centrifugal pump
pressure
pump assembly
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17160831.8A
Other languages
German (de)
English (en)
Other versions
EP3376050A1 (fr
EP3376050C0 (fr
Inventor
Thomas Blad
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grundfos Holdings AS
Original Assignee
Grundfos Holdings AS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Grundfos Holdings AS filed Critical Grundfos Holdings AS
Priority to EP17160831.8A priority Critical patent/EP3376050B1/fr
Priority to US16/492,755 priority patent/US11555499B2/en
Priority to CN201880018440.6A priority patent/CN110431313B/zh
Priority to PCT/EP2018/056078 priority patent/WO2018166967A1/fr
Publication of EP3376050A1 publication Critical patent/EP3376050A1/fr
Application granted granted Critical
Publication of EP3376050B1 publication Critical patent/EP3376050B1/fr
Publication of EP3376050C0 publication Critical patent/EP3376050C0/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/006—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps double suction pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0016—Control, e.g. regulation, of pumps, pumping installations or systems by using valves mixing-reversing- or deviation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/48—Fluid-guiding means, e.g. diffusers adjustable for unidirectional fluid flow in reversible pumps
    • F04D29/486—Fluid-guiding means, e.g. diffusers adjustable for unidirectional fluid flow in reversible pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/10—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system
    • F24D3/105—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system pumps combined with multiple way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/02—Fluid distribution means
    • F24D2220/0207—Pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/02—Fluid distribution means
    • F24D2220/0235—Three-way-valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/14—Arrangements for connecting different sections, e.g. in water heaters 
    • F24H9/142—Connecting hydraulic components

Definitions

  • the invention relates to a centrifugal pump unit with an electric drive motor, an impeller driven by it and a valve element.
  • Centrifugal pump units are known that incorporate an integrated valve assembly which can be moved between two switching positions, for example, by different directions of rotation of the drive motor and thus by different flow directions within the pump housing. These valve assemblies can very easily switch between two possible flow paths on the outlet side of the pump unit. Switching between two flow paths on the suction side of the pump unit, however, is only possible with a complex mechanism.
  • US 2016/0258340 A1 Disclosure reveals a cooling water pump with an integrated valve assembly for switching the flow path between branches of a cooling water circuit.
  • the valve assembly comprises a rotatable valve element, which is rotatable via a linearly movable pressure cylinder and a gear.
  • the pressure cylinder can be pressurized via solenoid valves to cause movement of the pivoting valve element.
  • US 5924432 A discloses a further centrifugal pump unit which belongs to the prior art of the invention presented here.
  • the object of the invention is to improve a centrifugal pump unit with a valve element movable between at least two switching positions in such a way that, on the one hand, a simple design of the valve device and, on the other hand, a reliable movement of the valve element is ensured.
  • the centrifugal pump assembly comprises an electric drive motor and at least one impeller that can be driven by this electric drive motor.
  • the electric drive motor is preferably designed as a wet-running motor, i.e., as a motor with a canned tube between the stator and rotor. In such a motor, the rotor rotates in the fluid to be pumped.
  • the centrifugal pump assembly particularly with the use of a wet-running electric motor, can, for example, be used in a heating or air conditioning system. There, it can be used as a circulation pump assembly.
  • the centrifugal pump assembly according to the invention further comprises at least one valve element which can be moved directly or indirectly along a first path of motion between at least two switching positions by the electric drive motor that drives the impeller.
  • Direct movement can be achieved, for example, by a suitable detachable coupling, in particular a magnetic or mechanical coupling, between the rotor or impeller of the drive motor and the valve element.
  • Indirect movement can be caused, for example, by the fluid pumped by the impeller, by the fluid flow and/or the pressure of the fluid acting on the valve element in such a way that it can be moved. In this way, movement along a first path of motion between at least two switching positions is effected.
  • the path of motion can be linear, curved, or rotary.
  • the at least one valve element is designed and arranged such that at least a part or section of the valve element, in addition to being movable along the first path of movement, is also movable along a second path of movement which differs from the first path of movement. That is to say, it is a Movement of the valve element is possible in at least two different directions, preferably angled relative to each other.
  • the valve element, or a part thereof is movable between a released position, in which it is detached from at least one contact surface and, in particular, spaced apart, and a pressed position, in which it is pressed against the at least one contact surface.
  • the valve element In the released position, the valve element is movable, in particular along the first path of movement between the at least two switching positions. In the released position, the valve element can be spaced apart from the contact surface or positioned so that it can easily slide along the contact surface. In the second pressed position, however, the valve element rests so firmly against the contact surface that it is held in a previously assumed switching position, i.e., movement along the first path of movement is prevented. In the pressed position, the valve element is pressed against the contact surface in such a way that the friction between the valve element and the contact surface is greater than in the released position. This allows the centrifugal pump unit to be operated in the conventional manner by running the electric drive motor, in particular to regulate the speed, without the valve element leaving its previously assumed switching position.
  • valve element To move the valve element to a different switching position, it is first moved along the second path of motion into the released position, so that it can then move to a different switching position driven by the drive motor.
  • the movement along the second path of motion is preferably also initiated directly or indirectly by the electric drive motor. This movement can be pressure-dependent, so that when a predetermined output pressure of the centrifugal pump unit is exceeded, the valve element is pressed into the closed position. If the centrifugal pump unit operates at a lower pressure or differential pressure... When operated, movement of the valve element between the switching positions is possible.
  • either the valve element as a whole can be movable along the second path of movement, or only a section of the valve element can be movable along the second path of movement, for example, an elastically deformable section of the valve element, such as an elastic seal.
  • an elastically deformable section of the valve element such as an elastic seal.
  • the at least one valve element is preferably mechanically and/or hydraulically coupled to the drive motor such that it can be moved by the drive motor along the first and/or the second path of motion.
  • the movement along the first path of motion can be effected, for example, by a hydraulic flow generated by the impeller, whereby this flow acts on the valve element or moves it along in the direction of flow by friction.
  • a mechanical or magnetic coupling can be provided, in particular a friction-fit coupling.
  • Such a coupling can preferably be designed so that it can be disengaged depending on the pressure, i.e., it disengages when a certain output pressure of the pump unit is reached, allowing the drive motor to continue rotating unhindered without moving the valve element further.
  • the valve element can, for example, be moved purely depending on the pressure, whereby when a certain output pressure of the fluid pumped by the impeller is reached, this pressure acts on the valve element such that it moves against the pressure.
  • the contact surface is pressed and preferably held there by friction and/or positive locking, so that, in particular, a flow or other coupling cannot move the valve element further between the switching positions.
  • the different flow velocities or pressures on the outlet side of the impeller can be adjusted via a control device that controls the drive motor.
  • the control device is preferably designed to adjust, in particular, the speed and, more preferably, also the acceleration profiles of the drive motor.
  • the second path of motion preferably extends transversely to the first path of motion or transversely to a plane in which the second path of motion extends or runs.
  • the planes in which the paths of motion run are perpendicular to each other.
  • the first path of motion can be a rotational motion about an axis of rotation
  • the second path of motion can be a linear motion along this axis of rotation.
  • the axis of rotation about which the valve element is rotatable along the first path of motion extends parallel to or in alignment with the axis of rotation of the impeller. This allows for a particularly simple coupling between the drive motor and impeller on the one hand and the valve element on the other.
  • the valve element is advantageously mounted to allow rotation such that, in the released position, it can rotate about a bearing, and in particular a central bearing, between the at least two switching positions, and is preferably held rotationally fixed to the contact surface in the second, engaged position.
  • the central bearing is preferably designed such that, in the released position, the valve element rests primarily only on the bearing, making it particularly easy to rotate. Additionally, the valve element can It may also be held against a return element, which forces it into the released position.
  • the bearing is preferably permanently lubricated or lubricated by the fluid being pumped, thus ensuring particularly smooth operation.
  • the valve element forms a force-fit and/or positive-locking coupling with the contact surface, which prevents rotation and thus holds the valve element in the switched position.
  • the second path of motion is preferably a straight line, and more preferably a straight line extending parallel to or along the axis of rotation of the at least one valve element.
  • the valve element can thus be mounted to rotate in its central region, the mounting preferably being designed to allow a certain linear movement along the axis of rotation in order to enable movement along the second path of motion.
  • the at least one contact surface is preferably at least one sealing surface.
  • the sealing surface can, for example, be formed by a valve seat surrounding a valve opening of a flow path. By contacting this sealing surface with the valve element, a seal of the valve opening is simultaneously achieved. Additionally, the described frictional engagement to prevent movement of the valve element can be achieved through this contact. Alternatively or additionally, a sealing surface can also be arranged such that, when the valve element is located between the suction and pressure sides, it seals the suction side against the pressure side of the centrifugal pump assembly in its contact position.
  • At least one valve element has a pressure surface which is connected to a pressure side of the impeller in such a way that a pressure prevailing on the pressure side is transferred to the impeller.
  • the pressure surface acts and thus generates a pressure force acting on the valve element, wherein the pressure surface is positioned such that this pressure force is directed at least partially along the second path of movement of the valve element and, in particular, along the second path of movement towards the contact position.
  • a pressure force is generated that is high enough to displace the valve element or a section of the valve element from the released to the contact position and press it against the contact surface in order to hold the valve element there by force and/or friction and/or to ensure sufficient sealing when in contact with at least one sealing surface.
  • the valve element is coupled to at least one return element, in particular a return spring, which exerts a return force on the valve element along the second path of movement, particularly towards the released position.
  • the return element ensures that when the pump unit is switched off, the valve element is moved to a starting position, which preferably corresponds to the released position. In this position, the valve element is then, as described above, preferably freely movable between the switching positions.
  • the drive motor is driven in this state, it is possible to move the valve element between the switching positions by appropriately controlling the drive motor.
  • a force can be applied to the valve element that overcomes the return force in order to move the valve element into the closed position.
  • the function of the return element can be achieved by the elastic deformability of a section of the valve element that is movable along the second path of movement. The return function is then performed by elastic return forces.
  • the centrifugal pump unit can include a force-generating means that exerts a force on the valve element in the direction of one of at least two switching positions, wherein the force is preferably a spring force, a magnetic force, and/or gravity.
  • the switching position in the direction of which the force generated by the force-generating means is directed preferably constitutes an initial or rest position.
  • the force-generating means is preferably designed and arranged such that, when the centrifugal pump unit is at rest, it forces the valve element into this initial position or a predetermined switching position. From this position, the valve element can then be moved to another switching position by a suitable drive motor.
  • valve element can also be held in the switching position corresponding to the initial position even when the centrifugal pump unit is in operation. This can be achieved, for example, by very rapid acceleration of the drive motor, which directly creates such a pressure on the output side of the impeller that it can act on the valve element at a pressure surface and press it against the contact surface.
  • the coupling between the drive motor and the valve element is particularly preferably hydraulically designed, wherein the at least one valve element is preferably configured such that it can be moved along the first path of motion by a fluid flow set in motion by the impeller.
  • This fluid flow is particularly preferably a rotating fluid flow in the outlet region of the impeller, which surrounds the impeller as it rotates.
  • This flow can, for example, act on the valve element by friction and move it along with it, especially if the valve element is designed so that it can be rotated between switching positions about an axis of rotation corresponding to the axis of rotation of the impeller.
  • This hydraulic coupling has the advantage that, after reaching the desired switching position, the flow in the pump housing can continue unimpeded, while the valve element is held in the achieved switching position by a stop and/or contact with the contact surface. In this state, the flow on the surface of the valve element preferably only causes friction that corresponds to the normal friction inside the pump housing, so that the switching functionality results in essentially no additional power loss in the centrifugal pump unit.
  • the drive motor is designed, or can be controlled by a control device, such that it can be driven in two different directions of rotation.
  • the impeller is further preferably designed such that, depending on its direction of rotation, it generates differently directed fluid flows, by which the at least one valve element can be moved in opposite directions along the first path of movement.
  • the valve element can be moved back and forth between the at least two switching positions. If, as described above, a force-generating means is used to generate a force that moves the valve element...
  • valve element If the valve element is moved back to its initial position, this reversal of the direction of rotation of the drive motor can be dispensed with, since the return movement of the valve element is then carried out by the power generating means, while the movement from the initial position can be carried out via the drive motor in the manner described.
  • the drive motor has a control device which controls the drive motor in such a way that the speed and/or the acceleration and/or the direction of rotation of the drive motor can be specifically changed in order to achieve the processes described above.
  • the valve element can thus be held in the switching position corresponding to the initial position. If, on the other hand, the acceleration is slower, a pressure high enough is not reached to move the valve element along the second path of movement into the closed position. When the valve element is moved, a flow can initially develop which can move it to a different switching position as described. Thus, simply by controlling the drive motor, the valve element can be moved precisely into a desired switching position and held there for the continued operation of the pump unit.
  • the pressure at which the valve element comes into contact with the mating surface is preferably selected to be lower than the usual operating pressure of the centrifugal pump unit, so that the normal operation of the centrifugal pump unit is not affected after the switching position is reached.
  • the lubricating film can be formed, for example, by the fluid conveyed by the impeller.
  • the fluid is particularly preferably water.
  • a direction-dependent coupling is possible, which, for example, like a pawl or ratchet, only works in one direction of rotation, while in the opposite direction of rotation The coupling elements slide against each other.
  • a direction of rotation of the drive motor which preferably does not correspond to the normal direction of rotation of the impeller, can be used to move the valve element into a desired switching position, while in the other direction of rotation, which preferably corresponds to the normal operating direction, the coupling is inactive, so that the valve element remains in the achieved switching position.
  • a coupling can be used particularly preferably in combination with the force-generating device described above to generate a force that moves the valve element back to its initial position.
  • a hydraulic coupling between the impeller and the drive motor is also possible, as described above.
  • the at least one valve element can be designed and arranged such that, within a pump housing surrounding the impeller, it separates a suction chamber connected to a suction side of the impeller from a pressure chamber connected to the pressure side of the impeller.
  • the valve element can more preferably surround a suction inlet of the impeller in an annular manner.
  • the arrangement of the valve element between the suction and pressure sides has the advantage that the differential pressure between the suction and pressure sides can be used to move the valve element along the second path of motion.
  • the pressure-side pressure acts on one side of the valve element, while the suction-side pressure acts on the opposite side.
  • fluid flows to act on one or both sides of the valve element, i.e., on the pressure side and/or the suction side, to move the valve element along the first path of motion.
  • the at least one valve element is designed and arranged such that, within a pump housing surrounding the impeller, it separates a suction chamber connected to a suction side of the impeller from a pressure chamber connected to a pressure side of the impeller.
  • a flow generated by the impeller acts on the valve element, causing it to move along the first path of motion.
  • the suction chamber is designed such that the flow prevailing there exerts no force on the valve element in the direction of the first path of motion.
  • the valve element can be selectively driven or moved by the flow in the pressure chamber, preferably the flow surrounding the impeller, to move it between switching positions. On the suction side, less force or no opposing force acts.
  • it is also possible to design the suction-side flow paths such that the flow prevailing there exerts a corresponding force on the valve element, causing it to move.
  • the centrifugal pump assembly has at least two alternative flow paths, wherein the at least one valve element is arranged in these flow paths such that these flow paths are open differently in the at least two switching positions.
  • the valve element can function as a changeover valve by alternately opening the two flow paths. That is, in a first switching position, the first flow path is closed and the second flow path is open, while in a second switching position, the first flow path is open and the second flow path is closed.
  • the valve element can assume more than two switching positions, in which the flow paths are open to different degrees. It is preferably designed such that, when it is moved, it closes one flow path by a certain amount while simultaneously opening the other flow path by the same amount.
  • centrifugal pump unit according to the invention described in the following description relate to applications in heating and/or air conditioning systems in which a liquid heat transfer medium, in particular water, is circulated by the centrifugal pump unit.
  • the centrifugal pump unit comprises a motor housing 2 in which an electric drive motor is arranged.
  • This motor has, in a known manner, a stator 4 and a rotor 6, which is arranged on a rotor shaft 8.
  • the rotor 6 rotates in a rotor chamber, which is separated from the stator chamber, in which the stator 4 is arranged, by a canned tube or a canned housing 10.
  • This is a wet-running electric drive motor.
  • the motor housing 2 is connected to a pump housing 12, in which an impeller 14, non-rotatably connected to the rotor shaft 8, rotates.
  • a movable valve element 18 is arranged in the pump housing 12.
  • This valve element 18 is rotatably mounted on an axis 20 inside the pump housing 12 such that the axis of rotation of the valve element 18 is aligned with the axis of rotation X of the impeller 14.
  • the axis 20 is fixed to the bottom of the pump housing 12 to prevent rotation.
  • the valve element 18 is not only rotatable about the axis 20, but also movable to a certain extent in the longitudinal direction X. In one direction, this linear movement is limited by the pump housing 12, against which the valve element 18 abuts with its outer circumference. In the opposite direction, the movement is limited by the nut 22 with which the valve element 18 is fastened to the axis 20. It should be understood that instead of the Nut 22 could also be used for a different axial fastening of the valve element 18 on the axis 20.
  • the valve element 18 separates a suction chamber 24 from a pressure chamber 26 in the pump housing 12.
  • the impeller 14 rotates in the pressure chamber 26.
  • the pressure chamber 26 is connected to the pressure port or pressure nozzle 28 of the centrifugal pump unit, which forms the outlet of the centrifugal pump unit.
  • Two suction-side inlets 28 and 30 open into the suction chamber 24, of which inlet 28 is connected to a first suction port 32 and inlet 30 to a second suction port 34 of the pump housing 12.
  • the valve element 18 is disc-shaped and simultaneously functions as a conventional deflector plate, separating the suction chamber 24 from the pressure chamber 26.
  • the valve element 18 has a central suction opening 36 with a projecting circumferential collar that engages with the suction inlet 38 of the impeller 14 and is essentially in tight contact with it.
  • the valve element 18 is essentially smooth on the side facing the impeller 14. On the side facing away from the impeller 14, the valve element has two annular sealing surfaces 40, which in this embodiment are located on closed tubular nozzles.
  • the two annular sealing surfaces 40 are arranged at two diametrically opposite positions on the sealing element 18 with respect to its axis of rotation X, so that they can form tight contact in the circumferential region of the inlets 28 and 30 at the bottom of the pump housing 12 to seal the inlets 28 and 30.
  • Support elements 42 are arranged at an angle of 90° to the sealing surfaces 40. These elements can also come into contact with the circumference of the inlets 28 and 30, but are spaced apart from each other so that they do not obstruct the inlets 28 and 30.
  • the inlets 28 and 30 do not lie on a diameter line with respect to the axis of rotation X, but on a radially offset straight line, so that when the valve element 18 rotates about the axis of rotation X, in a first switching position the inlet 38 is closed by a sealing surface 40, while the support elements 42 lie against the inlet 30 and open it. In a second switching position, the inlet 30 is closed by a sealing surface 40, while the support elements 42 lie in the circumferential area of the inlet 28 and open it.
  • the first switching position in which the inlet 38 is closed and the inlet 30 is open, is in Fig. 5 shown.
  • the second switching position, in which input 30 is closed and input 28 is open, is shown in Fig. 6 This means that by rotating the valve element 90° around the axis of rotation X, the two switching positions can be changed.
  • the two switching positions are limited by a stop element 44, which alternately abuts two stops 46 in the pump housing 12.
  • a spring 48 presses the valve element 18 into a released position in which the outer circumference of the valve element 18 is not in tight contact with the pump housing 12 and the sealing surfaces 40 are not in tight contact with the circumferential area of the inlets 28 and 30, so that the valve element 18 can rotate about the axis 20.
  • the control unit 17 in the electronic housing 16 sets the drive motor in motion, causing the impeller 14 to rotate, a circulating flow is generated in the pressure chamber 26, which, via friction, rotates the valve element 18 in its direction of rotation.
  • the control unit 17 is designed to drive the drive motor in either of two directions of rotation.
  • valve element 18 can be moved about the axis of rotation X in two directions, depending on the direction of rotation of the impeller 14, by means of the flow set in rotation by the impeller 14, since the flow in the circumferential region of the impeller 14 always flows in its direction of rotation.
  • the valve element 18 can be moved between the two switching positions limited by the stops 46 can be rotated.
  • the support elements 42 come into contact, keeping this inlet open and allowing a flow path from this inlet 28, 30 to the suction opening 36 and from there into the interior of the impeller 14.
  • a frictional connection is simultaneously created between the valve element 18 and the pump housing 12. This frictional connection ensures that the valve element 18 is held in the achieved switching position. This makes it possible to briefly switch off the drive motor and restart it in the opposite direction of rotation without rotating the valve element 18. If the motor is switched off and restarted quickly enough, the pressure in the pressure chamber 26 does not decrease to such an extent that the valve element 18 can move axially back to its released position.
  • the described centrifugal pump unit according to the first embodiment of the invention can, for example, be used in a heating system such as that found in Fig. 7 As shown, such a heating system is typically used in apartments or houses and serves to heat the building and provide hot water.
  • the heating system has a heat source 52, for example, in the form of a gas boiler.
  • a heating circuit 54 is present, which, for example, runs through various radiators in a building.
  • a secondary heat exchanger 56 is provided, via which domestic hot water can be heated.
  • a diverter valve is usually required, which directs the heat transfer fluid flow either through the heating circuit 54 or the secondary heat exchanger 56.
  • this valve function is performed by the valve element 18, which is integrated into the centrifugal pump unit 1.
  • Control is carried out by the control unit 17 in the electronics housing 16.
  • the heat source 52 is connected to the pressure port 27 of the pump housing 12.
  • a flow path 58 is connected to the suction port 32, while a flow path 60 through the heating circuit 54 is connected to the suction port 34.
  • the second embodiment according to Figs. 8 to 10 differs from the first embodiment in the construction of the valve element 18'.
  • the valve element separates The pressure chamber 26 is separated from a suction chamber 24 of the pump housing 12.
  • the valve element 18 has a central suction opening 36' into which the suction mouth 38 of the impeller 14 engages in a sealing manner.
  • the valve element 18' has an opening 62 which, depending on the switching position of the valve element 18', can be selectively aligned with one of the inlets 28, 30.
  • the inlets 28', 30' differ in their shape from the inlets 28, 30 according to the preceding embodiment.
  • the valve element 18' has a central projection 64 which engages in a central hole 60 in the base of the pump housing 12 and is mounted there to rotate about the axis of rotation X. Simultaneously, the projection 64 in the hole 66 also allows axial movement along the axis of rotation X, which is limited in one direction by the base of the pump housing 12 and in the other direction by the impeller 14.
  • the valve element 18' has a pin 68 on its outer circumference, which engages in a semicircular groove 70 on the base of the pump housing 12. The ends of the groove 70 serve as stop surfaces for the pin 68 in the two possible switching positions of the valve element 18'.
  • the opening 62 In the first switching position, the opening 62 is located above the inlet 28', and in the second switching position, the opening 62 is located above the inlet 30', with the other inlet being closed by the base of the valve element 18'.
  • the rotational movement of the valve element 18' between the two switching positions is also effected in this embodiment by the flow generated by the impeller 14 in the pressure chamber 26.
  • projections 72 directed into the pressure chamber 26.
  • FIG. 11 shows another possible embodiment of the valve element 18".
  • This embodiment differs from the preceding embodiments in the construction of the valve element 18". It is designed as a valve drum.
  • the pump housing 12 essentially corresponds to the construction shown in Figure 1.
  • Figs. 1 to 6 wherein in particular the arrangement of the inlets 28 and 30 corresponds to the arrangement described with reference to the first embodiment.
  • the valve drum of the valve element 18" consists of a pot-shaped lower part, which is closed by a cover 78.
  • the cover 78 faces the pressure chamber 26 and has the central suction opening 36, which engages with its axially directed collar in the suction mouth 38 of the impeller 14.
  • This axial position is also limited in this embodiment by the nut 22.
  • the valve element 18 As described above, is rotatable by the flow caused by the impeller 14, i.e., a hydraulic coupling is established between the impeller 14 and the valve element 18".
  • the engaged position which in Fig. 12 As shown, depending on the switching position, one of the inputs 28, 30 is tightly closed. Furthermore, a seal is also created between the suction chamber 24 and the pressure chamber 26 by the contact of the valve element 18" with the system shoulder 50.
  • FIG. 14 and 15 Figure 1 shows a fourth embodiment in which the design of the pump housing 12 corresponds to that of the pump housing 12 according to the first and third embodiments.
  • the rotary movement of the valve element 18c is assisted by the suction-side flow, that is, the flow entering the suction inlet 38 of the impeller 14.
  • the valve element 18c is essentially drum-shaped and has a cover 28 facing the pressure chamber 26 with the central suction opening 36, which engages with the suction inlet 38 as described above.
  • the lower part 76b shown here has two inlet openings 80.
  • one of the inlets 28, 30 can be overlapped, with the other inlet 28, 30 being tightly closed by the base of the lower part 46b, as described in the preceding embodiment.
  • a guide wheel 86 with blades is arranged between the lower part 76b and the cover 78. The flow from the inlet openings 80 enters radially into the guide wheel 86 and exits axially towards the central suction opening 36. The blades of the guide wheel 86 also generate a torque about the axis 20, which moves the valve element 18c between the switching positions. This functions essentially as described above.
  • a spring 48 as described above, can also be provided to move the valve element 18c into a released position.
  • the return movement in this embodiment is effected by a weight 88.
  • the centrifugal pump unit is always in the installation position shown in Fig. 15 The figure shows the axis of rotation X extending horizontally.
  • the valve element 18c When the centrifugal pump unit is switched off, the valve element 18c always rotates about the axis 20 such that the weight 88 is at the bottom. The torque generated by the guide wheel 86 can rotate the valve element 18c against this restoring force generated by the weight 88.
  • Very rapid activation of the drive motor allows pressure to build up so quickly in the pressure chamber 26 that the valve element 18c enters its closed position, as described above, in which it is held firmly against the pump housing 12 without being moved from its rest position. It should be understood that a return of the valve element by gravity or another restoring force, independent of the drive, could also be used in the other embodiments described here.
  • valve element 18d is conical.
  • the valve element 18d has a conical, pot-shaped lower part 76d, which is closed by a cover 78d.
  • the cover 78d has a central suction opening 36, which engages with the suction inlet 38 of the impeller 14 as described above.
  • inlet openings 90 are formed in the conical circumferential surface of the lower part 76d.
  • Sealing surfaces 92 are formed on the conical lower part between the inlet openings 90, which can close the respective inlets.
  • the valve element 18d has a pin-shaped projection 64 which engages in a recess on the bottom of the pump housing 12 and mounts the valve element 18d there so that it rotates about the axis of rotation X.
  • the lower part 76d of the valve element 18d is essentially not in contact with the pump housing 12, so that it can be rotated by the flow in the pressure chamber 26, as described in the previously described embodiments.
  • a back-and-forth movement of the valve element 18d can again be achieved, whereby the rotational movement of the valve element 18d can again be limited by stops (not shown).
  • a tight seal of the valve element 18d is achieved, and secondly, it is held in a force-fit position, so that it again, as long as the pressure in the pressure chamber 26 is sufficiently high, it will not move between the switching positions even when the direction of rotation of the impeller 14 changes.
  • the sixth embodiment according to Figs. 19 to 22 is similar to embodiment 2 according to Figs. 8 to 10
  • the pump housing 12 essentially corresponds to the structure shown and described therein.
  • the motor housing 2 with the electronics housing 16 and the canned tube 10 also correspond to the structure according to the second embodiment.
  • the valve element 18e has a very similar structure to that of the valve element 18'. Only the projections 72 and the pin 74 are missing.
  • the opening 62 is designed in the same way.
  • the suction opening 36e also essentially corresponds to the structure of the suction opening 36'.
  • the valve element 18e is rotatably mounted on a hollow shaft, which is inserted into the hole 66 in the base of the pump housing 12.
  • the spring 48 is arranged inside the hollow shaft 94.
  • valve element 18e is additionally movable axially along the axis of rotation X, which is the axis of rotation of the impeller 14 and the valve element 18e.
  • Fig. 21 indicates the first switch position, in which is opposite the opening 62 and the entrance 28'
  • Fig. 22 shows the second switching position, in which the opening 62 is opposite the second input 30'.
  • the rotation of the valve element 18e is again effected via the impeller 14; however, a mechanical coupling is provided here, which is realized by the impeller 14, with its area surrounding the suction opening 38, frictionally engaging with the circumference of the suction opening 36e.
  • the valve element 18e rotates with the impeller 14 until the pin 68 reaches a stop.
  • the coupling disengages due to slippage.
  • the valve element 18e is then moved axially into its engaged position, as described above, whereby the coupling disengages from the impeller 14, allowing the impeller 14 to rotate essentially without friction.
  • the seventh embodiment according to Fig. 23 and 24 differs from the sixth embodiment described above in that a tongue 96 extending into the pressure chamber 26 is arranged on the valve element 18f, serving as an additional valve element within the pressure chamber 26.
  • the pump housing 12 has an additional pressure port 98, which opens into the pressure chamber 26 separately from the pressure port 27.
  • the tongue 96 can open either the pressure port 27 or the pressure port 28 and cover the other pressure port.
  • a pressure-side switching mechanism is provided on the pressure side of the impeller 14.
  • a mixing function can be simultaneously implemented via the inlets 28' and 30' by positioning the opening 92 so that, in a first switching position, it covers both inlets 28' and 30', allowing liquid from both inlets 28' and 30' to enter the pump housing. through the opening 62 and further through the suction port 38.
  • the opening 62 merely covers the inlet 28', while the inlet 30' is closed by the base of the valve element 18f as described above.
  • the pressure port 27 is closed and the pressure port 98 is opened.
  • the movement of the valve element 18f can be achieved as described above via the impeller 14 and a mechanical coupling, which disengages when the pressure in the pressure chamber 26 is sufficiently high due to axial displacement of the valve element 18f.
  • the valve element 18f is mounted on the rotor shaft 8.
  • the eighth embodiment according to Figs. 25 to 28 This embodiment differs from the sixth embodiment in the design of the mechanical coupling between the rotor shaft 8 and the valve element 18g.
  • the valve element 18g is mounted directly on the rotor shaft 8, which is extended and reaches into the hole 66 in the base of the pump housing 12.
  • two ring segments 100 with sliding bearing properties, in particular made of ceramic, are arranged inside the valve element 18g.
  • the ring segments 100 are held together by a clamping ring 102 and pressed against the rotor shaft 8.
  • the two ring segments 100 essentially form a 2/3 ring.
  • valve element 18g engages with a projection 104 on its inner circumference, so that the two ring segments 100 are arranged rotationally fixed inside the valve element 18g.
  • a passage 106 remains in the valve element 18g, which effects the valve function.
  • Passage 106 can be in a first switching position, which is in Fig. 27 shown, opposite the entrance 30' and in a second Switch position which is in Fig. 28
  • the valve element 18g is shown opposite inlet 28'.
  • the other inlet is closed.
  • the pressure prevailing in the pressure chamber 26 can press the valve element 18g axially against the base of the pump housing 2 surrounding inlets 28' and 30'.
  • valve element 18g The movement of the valve element 18g is effected by the drive of the impeller 14.
  • the rotor shaft 8 is positively engaged with the inner circumference of the ring segments 10 and rotates them, and thus the valve element 18g. Stops can be formed in the pump housing 12 for the two switching positions, as described above. If the valve element 18g reaches one of these stops, the pump shaft 8 slips inside the ring segments 100. As the rotational speed of the rotor shaft 8 increases, a lubricating film similar to that of a sliding bearing can form between the outer circumference of the rotor shaft 8 and the inner surfaces of the ring segments 100, allowing the rotor shaft 8 to rotate essentially frictionlessly inside the ring segments 100.
  • the drive motor is preferably driven by the control unit 17 at a lower speed than the speed at which the impeller 14 rotates during operation.
  • the drive motor can be driven in two directions of rotation in the manner described above, whereby, after reaching the desired switching position, it can be ensured by rapidly increasing the speed in the manner described above that the valve element 18g remains in the previously reached switching position due to the pressure in the pressure chamber 26 and its contact with the bottom of the pump housing 12.
  • a mechanical coupling is also provided between the drive motor and the valve element.
  • the drive motor can be controlled by the control unit 17 in two different operating modes. In a first operating mode, which corresponds to the normal operation of the circulation pump unit, the drive motor rotates in the conventional manner at a desired speed, which can be set, in particular, by the control unit 17. In the second operating mode, the drive motor is controlled in open-loop operation, so that the rotor can be rotated stepwise in individual angular increments of less than 360°. Thus, the drive motor can be moved in individual steps, similar to a stepper motor. In these embodiments, this is used to move the valve element precisely in small angular increments to a defined position, as described below.
  • the pump housing 2 incorporates a mixing valve, which can be used, for example, to adjust the temperature of underfloor heating.
  • the motor housing 2 with the electronics housing 16 corresponds to the previously described design.
  • the pump housing 12 is essentially constructed in the same way as the pump housing according to the first embodiment. Figs. 1 to 6 Only the external configuration differs.
  • the valve element 18h is also drum-shaped and consists of a pot-shaped lower part 76h, which is closed on its side facing the impeller 14 by a cover 78h. A suction opening 36 is formed in the central area of the cover 78h.
  • the valve element 18h is rotatably mounted on an axis 20, which is arranged in the base of the pump housing 12.
  • the axis of rotation of the valve element 18h as in the examples described above, is the axis of rotation X of the rotor shaft 8h.
  • the valve element 18h is also axially displaceable along the axis X and is held in position by a spring 48.
  • Fig. 33 The rest position shown is pressed, in which the valve element 18h is in a released position, in which the lower part 76h does not rest against the bottom of the pump housing 12, so that the valve element 18h is essentially free to rotate about the axis 20.
  • the end face of the rotor shaft 8h which is designed as a coupling 108, acts as an axial stop.
  • the coupling 108 engages with a mating coupling 110, which is arranged non-rotatably on the valve element 18h.
  • the coupling 108 has chamfered coupling surfaces which, along a circumferential line, essentially describe a sawtooth profile such that torque transmission from the coupling 108 to the mating coupling 110 is only possible in one direction of rotation, namely in the direction of rotation A.
  • Fig. 31 In the opposite direction of rotation B, the clutch slips, resulting in axial movement of the valve element 18h.
  • Direction of rotation B is the direction in which the pump unit is driven during normal operation.
  • Direction of rotation A is used for the targeted adjustment of the valve element 18h. This means that a direction-dependent clutch is designed here.
  • the counter-clutch 110 disengages from the clutch 108 due to the pressure in the pressure chamber 26.
  • a compressive force acts on the cover 78h, which opposes and exceeds the spring force of the spring 48, so that the valve element 18h is pressed into the engaged position, which is in Fig. 32
  • the lower part 76h rests against the bottom side of the pump housing 12, so that on the one hand the valve element 18h is held in a force-fit manner and on the other hand a tight system is achieved which seals the pressure and suction sides against each other in the manner described below.
  • the pump housing 12 has two suction ports 32 and 34, of which suction port 32 opens into an inlet 28h and suction port 34 into an inlet 30h in the base of the pump housing 12, i.e., into the suction chamber 24.
  • the lower part 76h of the valve element 18h has an arc-shaped opening 112 in its base, which extends substantially over 90°.
  • Fig. 34 Figure 1 shows a first switching position in which the opening 112 merely covers the inlet 30h, so that a flow path exists only from the suction port 34 to the suction opening 36 and thus to the suction mouth 38 of the impeller 14.
  • the second inlet 28h is tightly closed by the base of the valve element 18h, which rests against its circumference.
  • FIG. 36 The second switching position is shown, in which the opening 112 only covers the inlet 28h, while the inlet 30h is closed. In this switching position, only one flow path is open, from the suction port 32 to the suction nozzle 38.
  • Fig. 35 The diagram now shows an intermediate position in which opening 112 covers both inlets 28h and 30h, with inlet 30h only partially open. By changing the degree to which inlet 30h is open, the mixing ratio between the flows from inlets 28h and 30h can be altered.
  • the valve element 18h can also be adjusted in small steps by gradually moving the rotor shaft 8h to change the mixing ratio.
  • the centrifugal pump unit with the integrated valve, as described above, is shown in the diagram.
  • the hydraulic circuit has a heat source 114, for example a gas boiler, the outlet of which leads to, for example, the suction port 34 of the pump housing 12.
  • the pressure port 37 of the centrifugal pump unit 1 is connected to...
  • This example shows a floor heating circuit 116, the return of which is connected to both the inlet of the heat source 114 and the suction port 32 of the centrifugal pump unit.
  • a second circulation pump unit 118 can supply another heating circuit 120 with a heat transfer fluid that has the outlet temperature of the heat source 114.
  • the flow temperature of the floor heating circuit 116 can be regulated by mixing cold water from the return with the hot water at the outlet of the heat source 114.
  • the mixing ratio can be changed by rotating the valve element 18h, as described above, by altering the opening positions of inlets 28h and 30h.
  • the tenth embodiment according to Figs. 38 to 47 The diagram shows a centrifugal pump unit which, in addition to the mixing functionality described above, also has a switching functionality for the additional supply of a secondary heat exchanger for domestic hot water heating.
  • valve element 18i has, in addition to the opening 112, a through-channel 122 which extends from an opening 124 in the cover 78i to an opening in the base of the lower part 76i and thus connects the two axial ends of the valve element 18i.
  • the valve element 18i also has an arc-shaped bridging opening 126, open only towards the underside, i.e., towards the base of the lower part 76i and thus towards the suction chamber 24, which is closed towards the pressure chamber 26 by the cover 78i.
  • the pump housing 12 has, in addition to the pressure port 27 and the two previously described suction ports 34 and 32, a further port 128.
  • Port 128 opens into the suction chamber 24 via an inlet 130 in the base of the circulating pump unit 12, in addition to inlets 28h and 30h.
  • Figs. 43 to 46 The different switching positions are explained, with the cover 78i of the valve element 18i shown partially open in these figures to illustrate the position of the openings underneath.
  • Fig. 43 This shows a first switching position in which the opening 112 is opposite the inlet 30h, so that a flow connection is established from the suction port 34 to the suction opening 38 of the impeller 14. In the switching position according to Fig.
  • opening 112 is located above the inlet 130, thus creating a flow connection from the connection 128 to the suction opening 36 and via this to the suction mouth 38 of the impeller 14.
  • opening 112 lies above inlet 30h, thus establishing a flow connection from suction port 34 to the suction opening 38 of the impeller 14.
  • opening 124 and through-hole 122 partially overlap inlet 28h, creating a connection between pressure chamber 26 and suction port 32, which here functions as a pressure port.
  • bridging opening 126 covers inlet 130 and part of inlet 28h, thus also creating a connection from port 128 via inlet 130, bridging opening 126, and inlet 28h to port 32.
  • Fig. 46 This shows a fourth switching position in which the through channel 122 completely covers the input 28h, so that the connection 32 is connected to the pressure chamber 26 via the through channel 122 and the opening 124. At the same time, the bridging opening is covered. Entrance 126 now only covers entrance 130. Opening 112 still covers entrance 30h.
  • Such a centrifugal pump unit can be used, for example, in a heating system, as is the case in Fig. 47
  • the dashed line defines the centrifugal pump unit 1, as shown by the... Figs. 38 to 46
  • the heating system has a primary heat exchanger or heat source 114, which can be, for example, a gas boiler.
  • a first heating circuit 120 which can consist of conventional radiators, for example.
  • a flow path branches off to a secondary heat exchanger 56 for heating domestic hot water.
  • the heating system also has an underfloor heating circuit 116.
  • the return lines of the heating circuit 120 and the underfloor heating circuit 116 open into the suction port 34 on the pump housing 12.
  • the return line from the secondary heat exchanger 56 opens into the connection 128, which, as described below, offers two functionalities.
  • the connection 32 of the pump housing 12 is connected to the supply line of the underfloor heating circuit 116.
  • valve element 18i is in the first in Fig. 43 In the switching position shown, the impeller 14 pumps fluid from the suction port 34 via the pressure port 27 through the heat source 140 and the heating circuit 120 and back to the suction port 34. If the valve element 18i is in the second switching position, which is shown in Fig. 44 As shown, the system is switched to domestic hot water operation. In this state, the pump unit or impeller 14 pumps liquid from connection 128, which serves as the suction connection, through pressure connection 27, via the heat source 114, through the secondary heat exchanger 56, and back to connection 128. If the valve element 18i is in the third switching position, which is shown in Fig. 45 shown Additionally, the underfloor heating circuit 116 is supplied.
  • Fig. 45 In the switch position shown, fluid simultaneously flows through the bypass opening 126, via port 128 and inlet 130, into port 32. This means that water flows from the heat source 114 through the secondary heat exchanger 26 and port 128 to port 32. Since essentially no heat is drawn from the secondary heat exchanger 56 during this heating operation, hot water is mixed into port 32 in addition to the cold water flowing from the pressure chamber 26 through the through channel 122 to port 32. The amount of hot water mixed into port 32 can be varied by changing the valve opening via position 18i.
  • Fig. 46 Figure 1 shows a switching position in which the mixing is switched off and connection 32 is exclusively in direct contact with the pressure chamber 26. In this state, the water in the underfloor heating circuit 116 is circulated without heat input.
  • both switching between heating and domestic hot water heating can be achieved, as well as simultaneously supplying two heating circuits with different temperatures: a first heating circuit 120 with the output temperature of the heat source 114 and an underfloor heating circuit 116 with a temperature reduced by a mixing function.
  • valve element is arranged directly in the pump housing; that is, the pump housing forms a combined pump and valve housing.
  • pump housing could also be designed in multiple parts.
  • valve element could also be arranged in a housing separate from the pump housing, which is connected to the pump housing, in which the impeller rotates, only via suitable connecting channels or pipes.

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Claims (20)

  1. Ensemble de pompe centrifuge avec un moteur d'entraînement électrique (4, 6), une roue (14) entraînée par celui-ci et au moins un élément de clapet (18), lequel peut être déplacé par le moteur d'entraînement électrique (4, 6) directement ou indirectement le long d'une première voie de déplacement entre au moins deux positions de fonctionnement,
    caractérisé en ce qu'
    au moins une partie de l'élément de clapet (18) peut être en plus déplacée le long d'une deuxième voie de déplacement différente de la première voie de déplacement entre une position débloquée, dans laquelle l'élément de clapet est à distance au moins d'une surface d'appui et une position appliquée, dans laquelle l'élément de clapet s'applique à au moins une surface d'appui, sachant qu'il est appuyé contre la surface d'appui de telle sorte que le frottement entre l'élément de clapet et la surface d'appui est plus grand que dans la position débloquée et le déplacement le long de la première voie de déplacement est empêché.
  2. Ensemble de pompe centrifuge selon la revendication 1, caractérisé en ce qu'au moins un élément de clapet (18) est couplé mécaniquement et/ou hydrauliquement au moteur d'entraînement (4, 6) de telle manière qu'il peut être déplacé par le moteur d'entraînement (4, 6) le
  3. Ensemble de pompe centrifuge selon la revendication 1 ou 2, caractérisé en ce que la deuxième voie de déplacement passe transversalement à la première voie de déplacement ou transversalement à un plan, dans lequel s'étend la deuxième voie de déplacement.
  4. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un élément de clapet (18) peut tourner le long de la première voie de déplacement autour d'un axe de rotation (X), sachant que l'axe de rotation (X) s'étend de préférence parallèlement à ou le long de l'axe de rotation (X) de la roue (14).
  5. Ensemble de pompe centrifuge selon la revendication 4, caractérisé en ce qu'au moins un élément de clapet (18) est logé pouvant tourner de telle manière qu'il peut tourner dans la position débloquée d'un positionnement et en particulier d'un positionnement central entre au moins les deux positions de fonctionnement et est de préférence maintenu dans la deuxième position appliquée solidaire en rotation sur la surface d'appui.
  6. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce que la deuxième voie de déplacement est une droite (X).
  7. Ensemble de pompe centrifuge selon l'une quelconque des revendications 4 à 6, caractérisé en ce que la deuxième voie de déplacement passe parallèlement à ou le long de l'axe de rotation (X) d'au moins un élément de clapet (18).
  8. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins une surface d'appui est une surface étanche.
  9. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un élément de clapet (18) comporte une surface de pression, laquelle se trouve en liaison avec un côté de pression (26) de la roue (14) de telle manière qu'une pression régnant sur le côté pression (26) agit sur la surface de pression et produit de ce fait une force de pression agissant sur l'élément de clapet (18), sachant que la surface de pression est placée de telle sorte que la force de pression est orientée au moins en partie le long de la deuxième voie de déplacement de l'élément de clapet (18) et est en particulier orientée le long de la deuxième voie de déplacement vers la position appliquée.
  10. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un élément de clapet (18) est couplé avec au moins un élément de rappel (48), en particulier un ressort de rappel, lequel exerce sur l'élément de clapet (18) une force de rappel le long de la deuxième voie de déplacement, en particulier vers la position débloquée.
  11. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé par un moyen de génération de force, lequel exerce sur l'élément de clapet une force en direction d'une des positions de fonctionnement, sachant que la force est de préférence une force élastique, une force magnétique et/ou de gravité.
  12. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un élément de clapet (18) est constitué de telle manière qu'il peut être déplacé par un écoulement de fluide décalé en déplacement par la roue (14) le long de la première voie de déplacement.
  13. Ensemble de pompe centrifuge selon la revendication 12, caractérisé en ce qu'il est constitué de telle manière que la roue (14) génère indépendamment de son sens de rotation des écoulements de fluide différemment orientés, par lesquels au moins un élément de clapet (18) peut être déplacé dans des sens opposés le long de la première voie de déplacement.
  14. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il comporte un système de commande (17), lequel commande le moteur d'entraînement électrique (4, 6) de telle manière que le nombre de tours et/ou le sens de rotation du moteur d'entraînement (4, 6) peut être modifié.
  15. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un élément de clapet (18) peut être déplacé par un écoulement généré par la roue (14) le long de la première voie de déplacement et peut être déplacé le long de la deuxième voie de déplacement par une pression de fluide générée par la roue (14), et le moteur d'entraînement (4, 6) comporte de préférence un système de commande (17), lequel est configuré de telle manière que le moteur d'entraînement (4, 6) peut être mis en marche avec une première allure d'accélération, à laquelle la pression s'établit plus rapidement que l'écoulement et avec une deuxième allure d'accélération à laquelle l'écoulement s'établit plus rapidement que la pression.
  16. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un élément de clapet (18) est couplé pour son déplacement le long de la première voie de déplacement à la roue (14) ou à un arbre (8) du moteur d'entraînement (4, 6) entraînant la roue (14) par le biais d'un accouplement, lequel peut être libéré de préférence en fonction de la pression et/ou de la vitesse de rotation et/ou du sens de rotation.
  17. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un élément de clapet (18) est constitué et disposé de telle manière que dans un corps de pompe (12) entourant la roue (14), il sépare un espace d'aspiration (24) en liaison avec un côté aspiration (24) de la roue (14) d'un espace de pression (26) en liaison avec un côté de pression de la roue (14).
  18. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un élément de clapet (18) est constitué et disposé de telle manière que dans un corps de pompe (12) entourant la roue (14), il sépare un espace d'aspiration (24) en liaison avec un côté aspiration de la roue (14) d'un espace de pression (26) en liaison avec un côté de pression de la roue (14), sachant que dans l'espace de pression (26) un écoulement généré par la roue (14) agit sur l'élément de clapet (18) pour le déplacement de celui-ci le long de la première voie de déplacement et l'espace d'aspiration (24) est constitué de telle manière que l'écoulement régnant dans celui-ci n'exerce aucune force sur l'élément de clapet (18) en direction de la première voie de déplacement.
  19. Ensemble de pompe centrifuge selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il comporte au moins deux voies d'écoulement alternatives, sachant qu'au moins un élément de clapet (18) est disposé dans ces voies d'écoulement de telle sorte que dans au moins les deux positions de fonctionnement ces voies d'écoulement sont ouvertes de façon différente.
  20. Ensemble de pompe centrifuge selon la revendication 19, caractérisé en ce que les deux voies d'écoulement sont placées côté aspiration de la roue (14).
EP17160831.8A 2017-03-14 2017-03-14 Groupe pompe centrifuge Active EP3376050B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP17160831.8A EP3376050B1 (fr) 2017-03-14 2017-03-14 Groupe pompe centrifuge
US16/492,755 US11555499B2 (en) 2017-03-14 2018-03-12 Centrifugal pump assembly
CN201880018440.6A CN110431313B (zh) 2017-03-14 2018-03-12 离心泵机组
PCT/EP2018/056078 WO2018166967A1 (fr) 2017-03-14 2018-03-12 Ensemble pompe centrifuge

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EP17160831.8A EP3376050B1 (fr) 2017-03-14 2017-03-14 Groupe pompe centrifuge

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EP3376050B1 true EP3376050B1 (fr) 2026-01-21
EP3376050C0 EP3376050C0 (fr) 2026-01-21

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EP (1) EP3376050B1 (fr)
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EP3438556A1 (fr) * 2017-08-03 2019-02-06 Grundfos Holding A/S Dispositif de mélange, système de chauffage avec dispositif de mélange et procédé
EP3540233A1 (fr) * 2018-03-13 2019-09-18 Grundfos Holding A/S Groupe pompe centrifuge avec valve rotative
CN214741982U (zh) * 2020-12-09 2021-11-16 明达实业(厦门)有限公司 一种气泵调压调速控制电路
US20240227502A9 (en) * 2022-10-20 2024-07-11 Cooper-Standard Automotive Inc Pump with integrated valve and temperature sensor and a thermal management system including such a pump
DE102023105784B4 (de) * 2023-03-08 2024-10-31 Bühler Motor GmbH Pumpenventilanordnung
CN119042114A (zh) * 2024-08-01 2024-11-29 中国船舶集团有限公司第七一九研究所 一种加热泵体

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US5924432A (en) * 1995-10-17 1999-07-20 Whirlpool Corporation Dishwasher having a wash liquid recirculation system

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KR100220407B1 (ko) 1996-10-28 1999-09-15 전주범 유로전환 하우징을 지닌 온수순환펌프
CN2418287Y (zh) 2000-02-01 2001-02-07 广东万家乐燃气具有限公司 自动换向泵
JP4287322B2 (ja) 2004-04-19 2009-07-01 朝日興業株式会社 ポンプ
EP2798224B2 (fr) 2011-12-27 2019-10-09 Grundfos Holding A/S Groupe de pompe
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US5924432A (en) * 1995-10-17 1999-07-20 Whirlpool Corporation Dishwasher having a wash liquid recirculation system

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US11555499B2 (en) 2023-01-17
US20200072223A1 (en) 2020-03-05
WO2018166967A1 (fr) 2018-09-20
EP3376050A1 (fr) 2018-09-19
EP3376050C0 (fr) 2026-01-21
CN110431313B (zh) 2021-06-18
CN110431313A (zh) 2019-11-08

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